U.S. patent number 9,162,349 [Application Number 13/590,619] was granted by the patent office on 2015-10-20 for torque limiter for a power tool.
This patent grant is currently assigned to MAKITA CORPORATION. The grantee listed for this patent is Hiroki Ikuta, Hikaru Sunabe. Invention is credited to Hiroki Ikuta, Hikaru Sunabe.
United States Patent |
9,162,349 |
Ikuta , et al. |
October 20, 2015 |
Torque limiter for a power tool
Abstract
A grinder as a power tool has a torque limiter. The torque
limiter includes a second bevel gear; a spindle; a flange to which
the rotation of the second bevel gear is transmitted, and a
plurality of balls which are disposed between the second bevel gear
and the flange. The ball is positioned at a first region and the
second bevel gear, the ball and the flange rotate integrally
thereby the rotation is transmitted to the flange. In a state that
a torque exerted on the spindle exceeding the predetermined
threshold, a relative rotation between the second bevel gear and
the flange is occurred and the ball moves from the first region to
the second region while rolling by means of the relative rotation.
Therefore, the transmission of the rotation from the second bevel
gear to the flange is regulated, and the torque exerted on the
spindle is regulated.
Inventors: |
Ikuta; Hiroki (Anjo,
JP), Sunabe; Hikaru (Anjo, JP) |
Applicant: |
Name |
City |
State |
Country |
Type |
Ikuta; Hiroki
Sunabe; Hikaru |
Anjo
Anjo |
N/A
N/A |
JP
JP |
|
|
Assignee: |
MAKITA CORPORATION (Anjo-shi,
JP)
|
Family
ID: |
46939496 |
Appl.
No.: |
13/590,619 |
Filed: |
August 21, 2012 |
Prior Publication Data
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|
|
Document
Identifier |
Publication Date |
|
US 20130048330 A1 |
Feb 28, 2013 |
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Foreign Application Priority Data
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|
|
|
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Aug 25, 2011 [JP] |
|
|
2011-184189 |
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Current U.S.
Class: |
1/1 |
Current CPC
Class: |
B25B
23/141 (20130101); B25D 16/003 (20130101); F16D
7/08 (20130101); B25D 2250/165 (20130101) |
Current International
Class: |
F16D
7/08 (20060101); B25B 23/14 (20060101); F16D
7/06 (20060101); B25D 16/00 (20060101) |
Field of
Search: |
;173/216,213,217 |
Foreign Patent Documents
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|
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2069073 |
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Aug 1981 |
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GB |
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A-2007-326168 |
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Dec 2007 |
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JP |
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Other References
Jan. 5, 2015 Office Action issued in Japanese Application No.
2011-184189. cited by applicant.
|
Primary Examiner: Lopez; Michelle
Attorney, Agent or Firm: Oliff PLC
Claims
What is claimed is:
1. A power tool which is adapted to actuate a tool being attachable
to the power tool, comprising: a motor; and a torque limiter which
is disposed between the motor and the tool, the torque limiter
including a driving rotational member; a driven rotational member
including a rotational shaft, the driven rotational member to which
a rotation of the driving rotational member is transmitted; and a
plurality of roll members which is disposed between the driving
rotational member and the driven rotational member, wherein the
torque limiter is adapted to regulate a transmission of the
rotation from the driving rotational member to the driven
rotational member in a state that a torque exerted on the
rotational shaft exceeds the predetermined threshold, wherein each
roll member is movable between a first region where the roll member
is located to transmit the rotation to the driven rotational member
and a second region where the roll member is located to regulate
the transmission of the rotation to the driven rotational member,
wherein the roll member transmits the rotation to the driven
rotational member in a state that the roll member is located at the
first region by rotating integrally with the driving rotational
member and the driven rotational member in a circumferential
direction of the rotational shaft, wherein in a state that the
torque exerted on the rotational shaft exceeds the predetermined
threshold, the driving rotational member and the driven rotational
member cause a relative rotation between the driving rotational
member and the driven rotational member, and the roll member is
moved from the first region to the second region while rolling
caused by the relative rotation, wherein the transmission of the
rotation to the driven rotational member is regulated in a state
that the roll member is located at the second region, wherein the
torque limiter includes a biasing member which biases the driving
rotational member and the driven rotational member to be close to
each other, wherein the driving rotational member includes a first
groove, a second groove which is deeper than the first groove and a
driving incline groove which includes an incline surface inclining
against a rotating surface of the driving rotational member, the
first groove, the second groove and the driving incline groove
being respectively contactable with the roll member, and wherein
the first groove and the second groove are connected via the
driving incline groove such that the first groove, the second
groove and the driving incline groove are disposed in a continuous
manner in a circumferential direction of the driving rotational
member, wherein the driven rotational member includes a third
groove corresponding to the first groove, a fourth groove
corresponding to the second groove and being deeper than the third
groove and a driven incline groove which includes an incline
surface inclining against a rotating surface of the driven
rotational member, the third groove, the fourth groove and the
driven incline groove being respectively contactable with the roll
member, and wherein the third groove and the fourth groove are
connected via the driven incline groove such that the third groove,
the fourth groove and the driven incline groove are disposed in a
continuous manner in a circumferential direction of the driven
rotational member, wherein a first part defined by a predetermined
part of the driving incline groove and a second part defined by a
predetermined part of the driven incline groove provide the first
region, and wherein the first groove, the second groove, a part
except the first part of the driving incline groove and the third
groove, the fourth groove, a part except the second part of the
driven incline groove provide the second region.
2. The power tool according to claim 1, wherein the biasing member
always biases the driving rotational member and the driven
rotational member to be close to each other.
3. The power tool according to claim 1, wherein the torque limiter
includes a cushion member which is disposed between the driving
rotational member and the driven rotational member, wherein a
thickness of the cushion member is defined such that the cushion
member contacts with one of the driving rotational member and the
driven rotational member in a state that the roll member contacts
with the first groove, and contacts with both of the driving
rotational member and the driven rotational member in a state that
the roll member contacts with the second groove.
4. The power tool according to claim 3, wherein the second groove
is disposed at a plurality of areas which are located at regular
intervals in the circumferential direction of the driving
rotational member, said plurality of areas corresponding to said
plurality of roll members respectively, wherein the cushion member
includes a plurality of holding portions which hold said plurality
of roll members respectively such that said plurality of roll
members are held at regular intervals.
5. The power tool according to claim 1, wherein the torque limiter
includes a retainer which is disposed between the driving
rotational member and the driven rotational member, the retainer
retaining said plurality of roll members such that said plurality
of roll members are located at regular intervals in a rotational
direction of the rotational shaft.
6. The power tool according to claim 1, wherein a length of the
second groove in a circumferential direction is defined such that
the roll member is regulated to move on the second groove in the
rotational direction.
7. The power tool according to claim 1, wherein the driving
rotational member includes a gear portion to which a rotational
output of a rotational driving mechanism is transmitted.
8. A power tool which is adapted to actuate a tool being attachable
to the power tool, comprising: a motor; and a torque limiter which
is disposed between the motor and the tool, the torque limiter
including a driving rotational member; a driven rotational member
including a rotational shaft, the driven rotational member to which
a rotation of the driving rotational member is transmitted; and a
plurality of roll members which is disposed between the driving
rotational member and the driven rotational member, wherein the
torque limiter is adapted to regulate a transmission of the
rotation from the driving rotational member to the driven
rotational member in a state that a torque exerted on the
rotational shaft exceeds the predetermined threshold, wherein each
roll member is movable between a first region where the roll member
is located to transmit the rotation to the driven rotational member
and a second region where the roll member is located to regulate
the transmission of the rotation to the driven rotational member,
wherein the roll member transmits the rotation to the driven
rotational member in a state that the roll member is located at the
first region by rotating integrally with the driving rotational
member and the driven rotational member in a circumferential
direction of the rotational shaft, wherein in a state that the
torque exerted on the rotational shaft exceeds the predetermined
threshold, the driving rotational member and the driven rotational
member cause a relative rotation between the driving rotational
member and the driven rotational member, and the roll member is
moved from the first region to the second region while rolling
caused by the relative rotation, wherein the transmission of the
rotation to the driven rotational member is regulated in a state
that the roll member is located at the second region, wherein the
torque limier includes a biasing member which biases the driving
rotational member and the roll member to be close to each other,
and a thrust bearing which is disposed between the biasing member
and the driven member, wherein the driven rotational member
includes a pressing member which presses the roll member against
the driving rotational member by transmitting a biasing force of
the biasing member exerted via the thrust bearing to the roll
member, and a transmission member which transmits the rotation to
the rotational shaft, wherein the driving rotational member
includes a first groove, a second groove which is deeper than the
first groove and a connect groove which includes a cross surface
crossing the a rotating surface of the driving rotational member,
the first groove, the second groove and the connect groove being
respectively contactable with the roll member, and wherein the
first groove and the second groove are connected via the connect
groove such that the first groove, the second groove and the
connect groove are disposed in a continuous manner in a
circumferential direction of the driving rotational member, wherein
a part of the connect groove provides the first region, and wherein
the first groove, the second groove and the other part of the part
of the connect groove provide the second region.
9. The power tool according to claim 8, wherein the torque limiter
includes a cushion member which is disposed between the pressing
member and the transmission member of the driven rotational member.
Description
CROSS REFERENCE TO RELATED APPLICATION
The present application claims priority from Japanese Patent
Application No. 2011-184189, filed on Aug. 25, 2011, the disclosure
of which is incorporated herein by reference in its entirety.
FIELD OF THE INVENTION
The invention relates to a power tool including a torque
limiter.
BACKGROUND OF THE INVENTION
Japanese non-examined Patent Application Publication No.
2007-326168 discloses a hammer drill having a torque limiter. The
torque limiter is provided with an intermediation gear actuated by
a driving gear; a driven flange including a plurality of fear cam
portions; balls held in a plurality of holding holes formed on the
intermediate gear with a predetermined interval in a
circumferential direction; a pressing plate, and a disc spring
pressing the pressing plate.
While the hammer drill is working, in a state that the torque
exerted on a hammer bit is less than the predetermined threshold,
the pressing plate presses the intermediate gear against the driven
flange by means of a biasing force of the disc spring and the
intermediate gear and the driven flange are rotated integrally,
thereby a torque of the intermediate gear is transmitted to the
driven flange. On the other hand, in a state that the torque
exerted on the hammer bit exceeds the predetermined threshold,
since the ball moves over the cam portion against the biasing force
of the disc spring, the pressing plate is pushed and the pressing
to the intermediate is cancelled, thereby a transmission of the
torque from the intermediate gear to the driven flange is
cancelled.
SUMMARY OF THE INVENTION
Problem to be Solved by the Invention
However, in the torque limiter disclosed in Japanese non-examined
Patent Application Publication No. 2007-326168, the ball is held by
means of the holding hole formed on the intermediate gear rotated
by the driving gear. And while the hammer drill is actuating, a
pushing force is exerted on the ball toward the center of the ball
from the intermediation gear in the lateral direction. In case that
the torque exceeding the predetermined threshold is exerted on the
hammer bit, since the ball receives a high biasing force from the
disc spring, the ball is pushed by the intermediation gear in the
lateral direction and then the ball moves on the driven flange
while sliding. As a result, due to a friction force between the
ball and the driven flange, a smooth driving of the torque is
disturbed.
An object of the invention is, in consideration of the above
described problem, to provide an improved technique with respect to
a torque limiter.
Means for Solving the Problem
Above-mentioned object is achieved by the claimed invention.
According to a preferable aspect of a power tool of the invention,
a power tool which is adapted to actuate a tool being attachable to
the power tool is provided. The power tool comprises a motor and a
torque limiter which is disposed between the motor and the tool.
The torque limiter comprises: a driving rotational member; a driven
rotational member including a rotational shaft, the driven
rotational member to which a rotation of the driving rotational
member is transmitted; and a plurality of roll members which is
disposed between the driving rotational member and the driven
rotational member. The torque limiter is adapted to regulate a
transmission of the rotation from the driving rotational member to
the driven rotational member in a state that a torque exerted on
the rotational shaft exceeds the predetermined threshold. Each roll
member is movable between a first region where the roll member is
located to transmit the rotation to the driven rotational member
and a second region where the roll member is located to regulate
the transmission of the rotation to the driven rotational member.
Further, the roll member transmits the rotation to the driven
rotational member in a state that the roll member is located at the
first region by rotating integrally with the driving rotational
member and the driven rotational member in a circumferential
direction of the rotational shaft. On the other hand, in a state
that the torque exerted on the rotational shaft exceeds the
predetermined threshold, the driving rotational member and the
driven rotational member cause a relative rotation between the
driving rotational member and the driven rotational member, and the
roll member is moved from the first region to the second region
while rolling caused by the relative rotation. And the transmission
of the rotation to the driven rotational member is regulated in a
state that the roll member is located at the second region. "The
transmission of the rotation to the driven rotational member is
regulated" of the invention preferably includes features that the
rotation of the driving rotational member transmitted to the driven
rotational member is reduced or interrupted, in comparison with a
situation in which the roll member is positioned at the first
region.
According to a the invention, the roll member moves from the first
region to the second region while rolling by means of a relative
rotation between the driving rotational member and the driven
rotational member, therefore in comparison in case that the roll
member moves while sliding against a friction force, a loss of the
energy for driving is decreased. Namely, the power tool in which
the torque limiter drives smoothly is provided. Further, the
degradation of the roll member is reduced thereby lifetime of the
torque limiter i.e. the power tool is extended.
According to a further preferable aspect of the power tool of the
invention, the torque limiter includes a biasing member which
biases the driving rotational member and the driven rotational
member to be close to each other. The driving rotational member
includes a first groove, a second groove which is deeper than the
first groove and a driving incline groove which includes an incline
surface inclining against a rotating surface of the driving
rotational member, the first groove, the second groove and the
driving incline groove being respectively contactable with the roll
member, and wherein the first groove and the second groove are
connected via the driving incline groove such that the first
groove, the second groove and the driving incline groove are
disposed in a continuous manner in a circumferential direction of
the driving rotational member. Further, the driven rotational
member includes a third groove corresponding to the first groove, a
forth groove corresponding to the second groove and being deeper
than the third groove and a driven incline groove which includes an
incline surface inclining against a rotating surface of the driven
rotational member, the third groove, the forth groove and the
driven incline groove being respectively contactable with the roll
member, and wherein the third groove and the forth groove are
connected via the driven incline groove such that the third groove,
the forth groove and the driven incline groove are disposed in a
continuous manner in a circumferential direction of the driven
rotational member. A first part defined by a predetermined part of
the driving incline groove and a second part defined by a
predetermined part of the driven incline groove provide the first
region. The first groove, the second groove, a part except the
first part of the driving incline groove and the third groove, the
forth groove, a part except the second part of the driven incline
groove provide the second region.
According to this aspect, since the roll member is positioned at
the first region and the driving rotational member, the roll member
and the driven rotational member are rotated integrally biased by
the biasing spring, the rotation of the driving rotational member
is transmitted to the driven rotational member. And in case that
the roll member moves to the second region, the roll member moves
from the driving incline groove to the driven incline groove while
rolling. Accordingly, the torque limiter is driven smoothly by a
simple composition which utilizes the first groove, the second
groove and the driving incline groove on the driving rotational
member, and the third groove, the forth groove, and the driven
incline groove on the driven rotational member, and the biasing
force of the biasing spring.
According to a further preferable aspect of the power tool of the
invention, the biasing member always biases the driving rotational
member and the driven rotational member to be close to each
other.
According to this aspect, in a state that the transmission of the
rotation to the driven rotational member is regulated, the roll
member is contacted with the driving rotational member and the
driven rotational member by the biasing force of the biasing
spring. Therefore, the roll member moves on the second region while
rolling steadily. Accordingly, the degradation of the roll member
is reduced. Further, the tilting rotation of the driving rotation
member and the driven rotational member are regulated by the
biasing force of the biasing spring.
According to a further preferable aspect of the power tool of the
invention, the torque limiter includes a cushion member which is
disposed between the driving rotational member and the driven
rotational member. A thickness of the cushion member is defined
such that the cushion member contacts with one of the driving
rotational member and the driven rotational member in a state that
the roll member contacts with the first groove, and contacts with
both of the driving rotational member and the driven rotational
member in a state that the roll member contacts with the second
groove.
According to this aspect, when the roll member moves from the first
groove to the second groove, the cushion member absorbs the impact
force occurred on the driving rotational member and the driven
rotational member.
According to a further preferable aspect of the power tool of the
invention, the second groove is disposed at a plurality areas which
are located at regular intervals in the circumferential direction
of the driving rotational member, said a plurality areas
corresponding to said a plurality of roll members respectively. The
cushion member includes a plurality of holding portions which hold
said a plurality of roll members respectively such that said a
plurality of roll members are held at regular intervals.
According to this aspect, the cushion member has a function for
keeping the interval of a plurality of the roll members. Therefore,
the number of the component utilized to the power tool is reduced.
Further, the transmission of the rotation to the driven rotational
member and the interruption of the transmission of the rotation are
accurately switched by said a plurality of the roll members held in
regular intervals.
According to a further preferable aspect of the power tool of the
invention, the torque limiter includes a retainer which is disposed
between the driving rotational member and the driven rotational
member, the retainer retaining said a plurality of roll members
such that said a plurality of roll members are located at regular
intervals in a rotational direction of the rotational shaft.
According to this aspect, since the retainer holds said a plurality
of the roll member in regular intervals, the transmission of the
rotation to the driven rotational member and the interruption of
the transmission of the rotation are accurately switched by said a
plurality of the roll members held in regular intervals. Therefore,
the torque limiter is worked smoothly.
According to a further preferable aspect of the power tool of the
invention, the torque limier includes a biasing member which biases
the driving rotational member and the roll member to be close to
each other, and a thrust bearing which is disposed between the
biasing member and the driven member. The driven rotational member
includes a pressing member which presses the roll member against
the driving rotational member by transmitting a biasing force of
the biasing member exerted via the thrust bearing to the roll
member, and a transmission member which transmits the rotation to
the rotational shaft. The driving rotational member includes a
first groove, a second groove which is deeper than the first groove
and a connect groove which includes a cross surface crossing the a
rotating surface of the driving rotational member, the first
groove, the second groove and the connect groove being respectively
contactable with the roll member, and wherein the first groove and
the second groove are connected via the connect groove such that
the first groove, the second groove and the connect groove are
disposed in a continuous manner in a circumferential direction of
the driving rotational member. A part of the connect groove
provides the first region. Further, the first groove, the second
groove and the other part of the part of the connect groove provide
the second region.
According to this aspect, the driven rotational member includes the
pressing member which presses the roll member against the driving
rotational member by transmitting the biasing force of the biasing
member exerted via the thrust bearing to the roll member, and the
transmission member which transmits the rotation to the rotational
shaft. Accordingly, when the rotation is transmitted via the
transmission member, the driving rotational member and the pressing
member rotate integrally, and when the transmission of the rotation
to the driven rotational member is regulated, a relative rotation
between the driving rotational member and the pressing member is
occurred thereby the roll member moves from the first region to the
second region while rolling. Therefore, the degradation of the roll
member is reduced. The lifetime of the torque limiter i.e. the
power tool is extended.
According to a further preferable aspect of the power tool of the
invention, the torque limiter includes a cushion member which is
disposed between the pressing member and the transmission member of
the driven rotational member.
According to this aspect, when the roll member moves from the first
groove to the second groove, the cushion member absorbs the impact
force occurred on the pressing member and the transmission
member.
According to a further preferable aspect of the power tool of the
invention, a length of the second groove in a circumferential
direction is defined such that the roll member is regulated to move
on the second groove in the rotational direction.
Before the power tool starts to work or after the power tool
drives, the roll member is positioned at the second groove.
Meanwhile, in a state that a free movement of the roll member is
allowed in the second groove, when the power tool starts or stops
to work, an inadvertent torque is exerted on the rotational shaft.
However, according to this aspect, since a length of the second
groove in a circumferential direction is defined such that the roll
member is regulated to move on the second groove in the rotational
direction, when the power tool starts or stops to work, an
inadvertent torque is not exerted on the rotational shaft, thereby
the torque limiter is worked smoothly.
According to a further preferable aspect of the power tool of the
invention, the driving rotational member includes a gear portion to
which a rotational output of a rotational driving mechanism is
transmitted. "A rotational driving mechanism" of the invention
typically includes feature in which a component such as a motor and
so on, which outputs a rotation preferably is included.
According to this aspect, the driving rotational member doubles
with a gear to which the rotational output of the rotational
driving mechanism is transmitted. Therefore, a number of the
component utilized on the power tool is reduced.
According to the invention, an improved technique with respect to a
torque limiter is provided.
Other objects, features and advantages of the invention will be
readily understood after reading the following detailed description
together with the accompanying drawings and the claims.
BRIEF DESCRIPTION OF THE DRAWINGS
FIG. 1 shows a cross-sectional view of a total composition of a
grinder in accordance with an embodiment of the invention.
FIG. 2 shows a cross-sectional view of a torque limiter in
accordance with a first embodiment of the invention.
FIG. 3 shows an exploded perspective view of the torque
limiter.
FIG. 4 shows a partial cross-sectional view of the torque limiter
along a circumferential direction of a second bevel gear and a
flange.
FIG. 5 shows a cross-sectional view taken from line V-V of FIG.
1.
FIG. 6 shows partial cross-sectional views along the
circumferential direction, which indicate a motion of the torque
limiter.
FIG. 7 shows a cross-sectional view of a torque limiter in
accordance with a second embodiment of the invention.
FIG. 8 shows an exploded perspective view of the torque
limiter.
FIG. 9 shows a partial cross-sectional view of the torque limiter
along a circumferential direction of a second bevel gear and a
flange.
FIG. 10 shows a cross-sectional view of the second embodiment of
the invention, which is corresponds to FIG. 5.
FIG. 11 shows partial cross-sectional views along the
circumferential direction, which indicate a motion of the torque
limiter.
DESCRIPTION OF THE PREFERRED EMBODIMENTS
Each of the additional features and method steps disclosed above
and below may be utilized separately or in conjunction with other
features and method steps to provide and manufacture improved power
tools and method for using such the power tools and devices
utilized therein. Representative examples of the invention, which
examples utilized many of these additional features and method
steps in conjunction, will now be described in detail with
reference to the drawings. This detailed description is merely
intended to teach a person skilled in the art further details for
practicing preferred aspects of the present teachings and is not
intended to limit the scope of the invention. Only the claims
define the scope of the claimed invention. Therefore, combinations
of features and steps disclosed within the following detailed
description may not be necessary to practice the invention in the
broadest sense, and are instead taught merely to particularly
describe some representative examples of the invention, which
detailed description will now be given with reference to the
accompanying drawings.
(First Embodiment)
A first embodiment of the invention will be explained with
reference to FIG. 1 to FIG. 6. In this embodiment, the invention
will be explained by applying to a grinder as one example of an
power tool. The grinder is configured to perform a grinding
operation, a sanding operation or a cutting operation against a
workpiece by rotating a grinding disc such as a grinding tool or a
sanding tool, or a cutting tool and so on.
As shown in FIG. 1, the grinder 1 is mainly provided with a main
housing 10, a gear housing 20, a wheel cover 30 and a rear
cover.
The main housing 10 is formed as a substantially cylindrical
housing, which houses a motor 100. A rotational shaft 101 of the
motor 100 is disposed so as to protrude toward the gear housing
20.
The gear housing 20 is arranged at one side of the main housing 10,
and houses a first bevel gear 200, a torque limiter 210 and a rock
member 270(refer to FIG. 5) and so on. The bevel gear 200 is
disposed at a periphery of the rotational shaft 101 of the motor
100. The torque limiter 210 includes a spindle 213 to which a
grinding disc 2 is attached. The rock member 270 is adapted to
regulate a rotation of the spindle 213 when the grinding disc 2 is
changed.
The wheel cover 30 is a substantially half-round shaped member
which is attachable to an outside of the gear housing 20. The wheel
cover 30 is adapted to surround a half periphery of the grinding
disc 2 attached on the spindle 213 in a circumferential direction.
The wheel cover 30 is adapted to regulate scatter of a workpiece
grinded by the grinding disc 2 and to protect a user from the
rotating grinding disc 2.
The rear cover 40 is arranged at opposite side of the main housing
10 opposed to the gear housing 20, and houses an electrical wiring
portion 300. The electrical wiring portion 300 is provided with a
power code 301 which provide current from an outside electrical
power source, and a switch 302 which is switchable ON/OFF of the
driving of the grinder 1. The electrical wiring portion 300 is
electrically connected to the motor 100.
The torque limiter 210 will be explained with reference to FIG. 2
to FIG. 4. As shown in FIG. 2, the torque limiter 210 is mainly
provided with a second bevel gear 211, a flange 212, a spindle 213,
balls 214, a ball retainer 215 and a biasing spring 216.
As shown in FIG. 2 and FIG. 3, the second bevel gear 211 is a
substantially disk-shaped member made of metal, and includes a
recess 220 is formed at a center part of the second bevel gear 211.
A through-hole 221, into which the spindle 213 penetrates, is
formed at the center of the recess 211. Further, gear teeth are
formed at the periphery which is outside of the recess 220 thereby
a gear portion 222 which is engaged with the first bevel gear 200
is provided by the gear teeth. The gear teeth of the gear portion
222 are not shown in FIG. 3 for convenience.
As shown in FIG. 3 and FIG. 4, a first cam groove 223 and a second
cam groove are disposed at a bottom surface of the recess 220 so as
to be connected via an incline groove 225a, 225b in a
circumferential direction of the second bevel gear 211 and form a
circle around the through-hole 221. The second cam grooves 224 are
disposed at six parts of the recess 220 in the circumferential
direction. The second cam groove 224 is deeper than the first cam
groove 223, and a length of the second cam groove 224 in the
circumferential direction is shorter than a length of the first cam
groove 223. The incline groove 225 includes an incline surface
which is inclined to the bottom surface of the recess 220. Namely,
the incline groove 225 is provided so as to be inclined to a
rotational surface of the second bevel gear 211. Further, an arrow
in FIG. 4 indicates a rotational direction of the second bevel gear
211. The second bevel gear 211 is a feature corresponding to "a
driving rotational member" of the invention. The first cam groove
223, the second cam groove 224 and the incline groove 225 are
features corresponding to "a first groove", "a second groove" and
"a driving incline groove" of the invention respectively.
The flange 212 is a disk-shaped member made of metal, and a
through-hole 230 with which the spindle 213 engages is formed at a
central part of the flange 212. A third cam groove 231 and a forth
cam groove 232 are disposed on an opposite surface (lower surface
in FIG. 4) of the flange 212 facing the second bevel gear 211, so
as to be connected via an incline groove 233a, 233b in a
circumferential direction of the flange 212, and form a circle
around the through-hole 230. The forth cam grooves 232 are disposed
at six parts of the flange 212 in the circumferential direction.
The forth groove 232 is deeper than the third groove 231. In this
way, a diameter of the circle defined by the third cam groove 231,
the forth cam groove 232 and the incline groove 233 corresponds to
a diameter of the circle defined by the first cam groove 223, the
second cam groove 224 and the incline groove 225 disposed on the
second bevel gear 221. The incline groove 233 includes an incline
surface which is inclined to a surface of the flange 212. Namely,
the incline groove 225 is provided so as to be inclined to a
rotational surface of the flange 212. An angle between the incline
surface of the incline groove 233 and the rotational surface of the
flange 212 is defined as a same angle value as an angle between the
incline surface of the incline groove 225 of the second bevel gear
211 and the rotational surface of the second bevel gear 211. The
third cam groove 231, the forth cam groove 232 and the incline
groove 233 are features corresponding to "a third groove", "a forth
groove" and "a driven incline groove" of the invention
respectively. Further, sections of the second bevel gear 211 and
the flange 211 are shown in FIG. 4, for convenience the ball 214
and the ball retainer 215 and so on and the other element are
omitted.
The spindle 213 is formed as a substantially cylindrical shape, and
includes an engaging groove 280 with which an engaging pin 234
engages, in a state that the engaging pin 234 is inserted to the
through-hole 230. The spindle 213 comes together with the flange
212 while the engaging pin 234 and the engaging groove 280 engage
with each other (refer to FIG. 5). The spindle 213 is a feature
corresponding to "a rotational shaft" of the invention. The flange
212 which is come together with the spindle 213 is a feature
corresponding to "a driven rotational member" of the invention.
The ball 214 is made of metal, and six balls are disposed
corresponding to the second cam groove 224. The ball retainer 215
is a disc-shaped member which is made of resin, a through-hole 240
to which the spindle 213 is inserted is disposed at the central
part of the ball retainer 215. Six ball holding holes 241 which
hold each ball 214 are disposed at regular intervals around the
through-hole 240 in the circumferential direction of the ball
retainer 215. This six ball holding holes 241 are disposed as same
intervals as the second cam groove 224. The ball 214 is a feature
corresponding to "a roll member" of the invention, the ball
retainer 215 is a feature corresponding to "a retainer" of the
invention. Further, the ball holding hole 241 is a feature
corresponding to "a holding portion" of the invention.
The biasing spring 216 is provided with two pairs of disc springs
250 and a plain washer 251. The plain washer 251 is disposed
between each pair of disc springs 250, each disc springs 250 of the
same pair of disc springs 250 is disposed so as to oppose to each
other. Number of the pair of disc springs 250 is optionally
changeable based on a necessity of amount of biasing force. The
biasing spring 216 is a feature corresponding to "a biasing member"
of the invention.
As shown in FIG. 2, the second bevel gear 211, the flange 212, the
spindle 213, the ball 214, the ball retainer 215 and the biasing
spring 216 are assembled and composed the torque limiter 210. The
second bevel gear 211 and the ball retainer 215 are assembled to be
relatively rotatable to the spindle 213. On the other hand, the
flange 212 and the biasing spring 216 are assembled to be rotated
integrally with the spindle 213. The ball 214 is movable along the
first cam groove 223, the second cam groove 224 and the incline
groove 225 of the second bevel gear 211, as well as the third
groove 231, the forth groove 232 and the incline groove 233 of the
flange 212. A nut 252 is screwed with a distal part of the spindle
213, the biasing force of the biasing spring 216 is adjustable by a
position of the nut 252. The biasing force biases the flange 212
and the second bevel gear 211 to be close to each other.
As shown in FIG. 1 and FIG. 2, the torque limiter 210 is held by
the gear housing 20 via two ball bearings 260 such that a one end
of the spindle 213 is protruded from the gear housing 20. Therefore
the torque limiter 210 is disposed in the gear housing 20 in which
a longitudinal direction of the spindle 213 and the rotational
shaft 101 of the motor 100 perpendicularly cross to each other.
As shown in FIG. 1, an inner flange 281 and an outer flange 282 are
disposed at a tip part of the spindle 213. The outer flange 282 is
screwed with the spindle 213 thereby the inner flange 281 and the
outer flange 282 clamp the grinding disk 2.
The torque limiter 210 is disposed to the grinder 1 described
above, the first cam groove 223, the second cam groove 224 and the
incline groove 225 are disposed at an opposite side from the
grinding disk 2 in the longitudinal direction of the spindle 213
with respect to the second bevel gear 211. Similarly, the gear
portion 222 is also disposed at the opposite side from the grinding
disk 2 with respect to the second bevel gear 211.
A locking member 270 will be explained with reference to FIG. 5.
The locking member 270 is provided with a locking pin 271, a press
cap 272 and a coil spring 273. The locking pin 271 is disposed to
be parallel to the longitudinal direction of the spindle 213 and to
penetrate the gear housing 20. A flange 274 is disposed on the
locking pin 271. The flange 274 prevents the locking pin 271 from
dropping off toward out of the gear housing 20. A tip of one side
of the locking pin 271 is adapted to engage with the engaging
recess 235 arranged on the flange 212 of the torque limiter
210.
The press cap 272 is arranged at a tip of the other side of the
locking pin 271 outside of the gear housing 20. The coil spring 273
is disposed around a periphery of the locking pin 271 outside of
the gear housing 20 such that one end of the coil spring 273
engages with the press cap 272 and the other end of the coil spring
273 engages with the coil spring engaging portion 21 arranged as a
concavity on an outside surface of the gear housing 20.
The locking member 270 described above is biased outward the gear
housing 20 by the biasing force of the coil spring 273. On the
other hand, the flange 274 prevents the locking member 270 from
dropping off by contacting with the gear housing 20. The tip of the
locking pin 271 is usually positioned distantly from the engaging
recess 235 of the flange 212.
When the press cap 272 is pressed against the biasing force of the
coil spring 273, the locking pin 271 is moved to be close to the
flange 212 and then the tip of the locking pin 271 is engaged with
the engaging recess 235. As a result, the motion of the flange 212
in the circumferential direction of the flange 212 is regulated.
Namely, when a user changes the grinding disk 2, the spindle 213 is
prevented from rotating.
The grinder 1 having a composition described above, an electric
power is provided to the motor 100 from the outside electrical
power source via the electrical wiring portion 300 by being
operated the switch 302. Therefore, the motor 100 drives
rotationally and the first bevel gear 200 arranged on the
rotational shaft 101 rotates. A rotational output of the motor 100
is changed into a rotation around the spindle 213 by rotating the
first bevel gear 200 and the second bevel gear 211 mated with each
other, the grinding disk 2 attached on the spindle 213 is rotated.
A workpiece is worked by pressing the rotating grinding disk 2 onto
the workpiece.
A motion of the torque limiter 210 will be explained with reference
to FIG. 6. Further, the second bevel gear 211, the flange 212, the
ball 214 and the ball retainer 215 of the torque limiter 210 are
only shown in FIG. 6, the other elements such like the biasing
spring 216 and so on are not shown for convenience. Further, only
one ball 214 is utilized for the explanation, however the motion of
the other balls 214 is same. An arrow A in the FIG. 6(b) to FIG.
6(f) shows a rotational direction of the second bevel gear 211. An
arrow B in the FIG. 6(c) to FIG. 6(f) shows a rotational direction
of the ball 214.
FIG. 6(a) shows one situation of the torque limiter 210 when the
grinder 1 is not working. In FIG. 6(a), the ball 214 contacts with
the second cam groove 224a and the ball retainer 215 contacts with
both of the second bevel gear 211 and the flange 212. Namely, a
thickness of the ball retainer 215 is defined such that the ball
retainer 215 contacts with both of the second bevel gear 211 and
the flange 212, when the ball contacts with the second cam groove
224 during the non-working time of the grinder 1. Therefore, when
the ball 214 contacts with the second cam groove 224, an top of the
ball 214 does not contacts with the forth cam groove 232a. Further,
a length of the second cam groove 224 is defined such that the
second cam groove 224 regulates a free movement of the ball 214 in
the rotational direction of the second bevel gear 224, when the
grinder 1 is not working.
FIG. 6(b) shows another situation of the torque limiter 210, when
the rotational output of the motor 100 is transmitted to the
spindle 213. The rotational output of the motor 100 is transmitted
to the second bevel gear 211 thereby the second bevel gear 211
rotates in a direction indicated by the arrow A. Due to the
rotation of the second bevel gear 211, the ball 214 moves to a
predetermined position where the ball 214 contacts with the incline
groove 225a of the second bevel gear 211 and the incline groove
233a of the flange 212 disposed to be parallel to each other. And
then, the second bevel gear 211, the ball 214 and the flange 212
rotate in an integral manner, thereby the rotation of the second
bevel gear 211 is transmitted to the spindle 213. Since the
grinding disk 2 attached on the spindle 213 is rotated, a workpiece
is worked. The part of the incline groove 225a, 233a with which the
ball 214 contacts are features respectively corresponding to "a
first region" of the invention.
FIG. 6(c) shows another situation of the torque limiter 210, a
transmission of rotation from the second bevel gear 211 to the
flange 212 is regulated when a torque exceeding a predetermined
threshold torque exerts on the spindle 213. For example, when the
grinding disk 2 bits a workpiece during the operation in the torque
limiter 210 shown in FIG. 6(b), a rotation of the grinding disk 2
is regulated. In accordance with the regulation of the transmission
of the rotation, the spindle 213 on which the grinding disk 2 is
attached and the flange 212 with which the spindle 213 is engaged
are also stopped rotating. On the other hand, because the motor 100
keeps rotating, the rotational output of the motor 100 is
transmitted to the second bevel gear 211. If the rotation of the
second bevel gear 211 is transmitted to the flange 212, the torque
exceeding to the predetermined threshold torque may exert on the
spindle 213 arranged between the grinding disk 2 regulated to
rotate and the flange 212.
However in this embodiment, a relative rotation between the second
bevel gear 211 and the flange 212 is occurred because the flange is
stopped rotating even though the second bevel gear 211 keeps
rotating. A rotate power on the ball 214 clamped between the second
bevel gear 211 and the flange 212 is occurred due to the relative
rotation. When the sum total of a component of the rotate power of
the six balls 214 in a direction being parallel to the spindle 213
exceeds the biasing force of the biasing spring 216, the ball 214
contacting with the inclined grooves 225a, 233a rotates while
pushing the flange 212, and moves to the position where the ball
214 contacts with the first cam groove 223 and the third cam groove
231. In this way, because the ball 214 is positioned on the first
cam groove 223 which is parallel to the rotational surface of the
second bevel gear 211, the transmission of the rotation from the
second bevel gear 211 to the flange 212 is regulated thereby the
torque exerted on the spindle 213 is reduced. Further, when the
ball 214 is positioned such that the ball 214 contacts with the
first cam groove 223 and the third cam groove 231, a gap t exists
between the flange 212 and the ball retainer 215.
Each FIG. 6(d) and FIG. 6(e) shows another situation of the torque
limiter 210 respectively after the ball 214 has moved to the
position where the ball 214 contacts with the first cam groove 223
and the third cam groove 231. Because of the relative rotation of
the second bevel gear 211 and the flange 212, the ball 214 moves
toward another second cam groove 224b which is located next to the
second cam groove 224a in the circumferential direction while the
ball 214 is rolling. Meanwhile, on the flange 212, the ball 214
moves toward another forth groove 232b which is located next to the
forth cam groove 232a in the circumferential direction. In each
FIG. 6(c) to FIG. (e), the biasing force of the biasing spring 216
is transmitted to the second bevel gear 211 from the flange 212 via
the ball 214. Namely, the biasing spring 216 always biases the
second bevel gear 211 and the flange 212 so as to be close to each
other.
FIG. 6(f) shows another situation of the torque limiter 210 in
which the ball 214 contacts with the incline groove 225b, 233b
respectively, when the ball 214 moves from the first cam groove 223
and the third cam groove 231 to the second cam groove 224b and the
forth cam groove 232b respectively. On the way of the ball 214 to
the second cam groove 224b and the forth cam groove 232b, the
flange 212 biased by the biasing spring 216 moves such that the gap
t becomes smaller and the flange 212 is close to the second bevel
gear 211, thereby the flange 212 contacts with the ball retainer
215. After that, the torque limiter 210 returns to the situation
shown by FIG. 6(b) in which the ball 214 contacts with the incline
groove 225a, 233a by passing the second cam groove 224b, and then
the similar cyclic behavior of the torque limiter 210 will be
repeated.
The rotation of the second bevel gear 211 is not transmitted to the
flange 212 in FIG. 6(c) to FIG. 6(f) respectively. Under these
situations, the first cam groove 223, the second cam groove 224 and
the incline groove 225b of the second bevel gear 221, and the third
cam groove 231, the forth cam groove 232 and the incline groove
233b of the flange 211 in which these grooves contacts with the
ball 214 respectively, is a feature corresponding to "a second
region" of the invention.
According to the first embodiment described above, because the ball
214 moves while rolling due to the relative rotation of the second
bevel gear 211 and the flange 212, the ball 214 can move smoothly.
Therefore, the torque limiter 210 works smoothly. Further, in
comparison with a composition in which the ball 214 moves while
sliding against the friction force, the degradation or the heat
generation of the ball 214 by the friction force is reduced.
Further, according to the first embodiment, because the ball 214 is
biased by the biasing spring 216 while the ball 214 is contacting
with the incline groove 255a, 233a, the second bevel gear 211, the
flange 212 and the ball 214 rotate integrally. Accordingly, a
simple construction in which grooves are formed on the second bevel
gear 211 and the flange 212 achieves that the torque limiter 210
works smoothly.
Further, according to the first embodiment, the biasing spring 216
always biases the second bevel gear 211 and the flange 212 so as to
be close to each other. Therefore, when the rotation of the second
bevel gear 211 is not transmitted to the flange 212, the second
bevel gear 211 is regulated to rotate while tilting against the
spindle 213.
Further, according to the first embodiment, the ball retainer 215
includes the ball holding hole 241 which holds the balls 214,
therefore the balls 214 are held in a same interval as the interval
of the second cam groove 224 and the forth cam groove 232. Namely,
the ball retainer 215 has a function for keeping the interval of
the balls 214.
Further, in a state that the ball retainer 215 is not provided to
the torque limiter 210, when the ball 214 moves from the first cam
groove 223 and the third cam groove 231 to the second cam groove
224 and the forth cam groove 232 respectively, because the second
bevel gear 211 and the flange 212 move to be close to each other,
both of the second bevel gear 211 and the flange 212 crash into the
ball 214. Accordingly, due to a crash of members made of metal,
when the torque limiter 210 is working, a noise or a metal fatigue
is occurred. However, in this embodiment, in a state that the ball
is positioned on the second cam groove 224, the ball retainer 215
contacts with both of the second bevel gear 211 and the flange 212.
Therefore, when the ball 214 moves from the first cam groove 223
and the third cam groove 231 to the second cam groove 224 and the
forth cam groove 232 respectively, the second bevel gear 211 and
the flange 212 are regulated to crash into the ball 214. Further,
an outside edge part of the flange 211 is regulated to crash into
the second bevel gear 211 directly. Further, because the ball
retainer 215 is made of resin, an impact power generated when the
second bevel gear 211 and the flange 212 made of metal respectively
crash into the ball retainer 215 is absorbed. Namely, the ball
retainer 215 has a function as a cushion member. Accordingly, the
ball retainer 215 is a feature corresponding to "a cushion member"
of the invention.
Further, according to the first embodiment, the length of the
second cam groove 224 in the circumferential direction is defined
such that the second cam groove 224 regulates the free movement of
the ball 214 in the rotational direction of the second bevel gear
211, when the grinder 1 is not working. In case that the free
movement of the ball 214 in the rotational direction of the second
bevel gear 211 may not be regulated, when the grinder 1 starts or
stops driving, a rotation differences between the second bevel gear
211 and the flange 212 may be occurred by the movement of the ball
214. Due to the rotation differences, an inadvertent torque may be
exerted on the spindle 213 or a failure of the driving of the
torque limiter 210 may be occurred when the grinder 1 starts or
stops driving. However, according to this embodiment, because the
length of the second cam groove 224 is defined such that the second
cam groove 224 regulates the free movement of the ball 214 in the
rotational direction of the second bevel gear 211 when the grinder
is not working, the inadvertent torque is not exerted and the
failure of the driving of the torque limiter 210 is not
occurred.
Further, according to the first embodiment, the first cam groove
223, the second cam groove 224 and the incline groove 225 are
disposed on the surface of the second bevel gear 211 opposed from
the side where the grinding disk 2 is attached. Therefore,
components of the torque limiter 210 such as the flange 212, the
ball 214 and the ball retainer 215 and so on, which are disposed to
oppose to the first cam groove 223, the second cam groove 224 and
the incline groove 225, are disposed on the surface opposed to the
side where the grinding disk 2 is attached with respect to the
second bevel gear 211. Therefore, a length of a part of the spindle
213 protruding in a direction from the second bevel gear 211 toward
the grinding disk 2 attached portion is shortened, thereby the
grinder 1 is downsized. Furthermore, since the gear teeth are
formed on the edge part of the second bevel gear 211, the recess
220 is formed at a central part of the second bevel gear 211. By
arranging components of the torque limiter 210 such as the flange
212, the ball 214, the ball retainer 215 and so on at the recess
220, each components are rationally arranged, thereby the torque
limiter 210 is downsized. As a result, the grinder 1 is
downsized.
Further, according to the first embodiment, the gear portion 222 is
formed at an opposite side from a side to which the grinding disk 2
is attached with respect to the longitudinal direction of the
spindle 213. Therefore, a length of the spindle 213 protruding from
the second bevel gear 211 is shortened, and as a result, the
grinder 1 is downsized. Further, since the gear portion 222, the
first cam groove 223, the second cam groove 224 and the incline
groove 225 are respectively arranged on the opposite side of the
second bevel gear 211 from where the grinding disk 2 is attached,
the components of the torque limiter 210 is rationally arranged.
Therefore, the grinder 1 is further downsized.
Further, in the first embodiment, the ball holding holes 241 which
keep an interval of the balls 214 is formed on the ball retainer
215, and the ball retainer 215 has functions as an interval keeping
member and a cushion member, however it is not limited to this
composition. The ball retainer may have only function as the
interval keeping member, and other cushion member may be provided
than the ball retainer 215.
(Second Embodiment)
A second embodiment will be explained with reference to FIG. 7 to
FIG. 11. However, same components as the first embodiment are
signed same numeral and omitted from the explanation for
convenience.
FIG. 7 shows a torque limiter 1210 according to the second
embodiment of the invention. Other components of the grinder 1 than
the torque limiter 1210 are similar to the first embodiment. The
torque limiter 1210 is mainly provided with a second bevel gear
1211, a rotation transmission member 1212a, a pressing force
transmission member 1212b, a spindle 1213, balls 1214, a cushion
member 1215, a biasing spring 1216, supporting balls 1217 and a
thrust bearing 1218.
As shown in FIG. 7 and FIG. 8, the second bevel gear 1211 is
similar to the second bevel gear 211 of the first embodiment,
namely a through-hole 1221, a first cam groove 1223, a second cam
groove 1224 and an incline groove 1225 are disposed annularly at a
bottom surface of a recess. Further, a supporting groove 1226 in
which the supporting balls 1217 are movable is at an outside of the
annular groove. A gear portion 1222 including gear teeth is
disposed at an outside of the recess 1220. Further, the gear teeth
are not shown in FIG. 8.
As shown in FIG. 9, the first cam groove 1223 and the second cam
groove 1224 are connected via the incline groove 1225 in the
circumferential direction. Further, an arrow in FIG. 9 indicates a
rotational direction of the second bevel gear 1211. Cross sections
of the second bevel gear 1211 and the pressing force transmission
member 1212b are shown in FIG. 9 for convenience, the other
elements such as the rotation transmission member 1212a, balls 1214
and so on are not shown in FIG. 9. The second bevel gear 1212 is a
feature corresponding to "a driving rotational member" of the
invention. The first cam groove 1223, the second cam groove 1224
and the incline groove 1225 are features respectively corresponding
to "a first groove", "a second groove" and "a connect groove" of
the invention.
As shown in FIG. 7 and FIG. 8, the rotation transmission member
1212a and the pressing force transmission member 1212b are
respectively disk-shaped members made of metal, of which
through-holes 1230a, 1230b to which the spindle 1213 is inserted
are respectively disposed at the center part. The cushion member
1215 is a disk-shaped member made of resin, of which a through-hole
1240 to which the spindle 1213 is inserted is disposed at the
center part. The cushion member 1215 is a feature corresponding to
"a cushion member" of the invention.
A cushion member holding portion 1236 is provided around the
through-hole 1230a of the rotation transmission member 1212a.
Engaging recesses 1235 which engage with the locking pin (refer to
FIG. 10) are disposed at three part of the periphery of the
rotation transmission member 1212a. Ball holding holes 1241 which
correspond to the size of the ball 1214 are disposed at six part of
the cushion member holding portion 1236. A third cam groove 1231 is
disposed on a surface (lower surface in FIG. 9) of the pressing
force transmission member 1212b which faces the second bevel gear
1211 in the circumferential direction. In the second embodiment,
only the third cam groove 1231 is disposed on the pressing
transmission member 1212b, i.e. the incline groove is not disposed.
Further, the rotation transmission member 1211a is a feature
corresponding to "a transmission member" of the invention. The
pressing force transmission member 1212b is a feature corresponding
to "a pressing member" of the invention.
The spindle 1213 is formed as a substantially cylindrical shape,
and includes an engaging groove 1280 with which an engaging
protrusion 1237 of the through-hole 1230a engages, in a state that
the spindle 1213 is inserted to the through-hole 1230a, 1240,
1230b. The spindle 1213 is a feature corresponding to "a rotational
shaft" of the invention. The rotation transmission member 1212a and
the pressing force transmission member 1212b which are incorporated
with the spindle 1213 are a feature corresponding to "a driven
rotational member" of the invention.
The ball 1214 is made of metal, and six balls are disposed
corresponding to the second cam groove 1224. Further, the
supporting ball 1217 is made of metal, and four balls are disposed
in the supporting groove 1226. The ball 1214 is a feature
corresponding to "a roll member" of the invention.
The biasing spring 1216 is provided with a pair of disc springs
1250 and a plain washer 1251. The plain washer 1251 is disposed
between the pair of disc springs 1250, the disc springs 1250 are
disposed so as to oppose to each other. In the first embodiment,
two pairs of the disc springs 250 are provided, however in the
second embodiment, one pair of the disc springs 1250 is provided.
Further, number of the pair of disc springs 1250 is optionally
changeable based on a necessity of amount of biasing force. The
biasing spring 1216 is a feature corresponding to "a biasing
member" of the invention.
As shown in FIG. 7, the second bevel gear 1211, the rotation
transmission member 1212a, the pressing force transmission member
1212b, the spindle 1213, the ball 1214, the cushion member 1215,
the biasing spring 1216, the supporting ball 1217 and the thrust
bearing 1218 are assembled and composed the torque limiter 1210.
The second bevel gear 1211, the pressing force transmission member
1212b, the cushion member 1215, the biasing spring 1216 and the
thrust bearing 1218 are assembled to be relatively rotatable to the
spindle 1213. On the other hand, the rotation transmission member
1212a is assembled to be rotated integrally with the spindle 1213.
The ball 1214 is movable along the first cam groove 1223, the
second cam groove 1224 and the incline groove 1225 of the second
bevel gear 1211. The supporting ball 1217 is movable along the
supporting groove 1226 of the second bevel gear 1211.
A nut 1252 is screwed with a distal part of the spindle 1213, the
biasing force of the biasing spring 1216 is adjustable by a
position of the nut 1252. The biasing force is transmitted to the
pressing force transmission member 1212b via the thrust bearing
1218, and biases the pressing force transmission member 1212b and
the second bevel gear 211 to be close to each other.
The supporting ball 1217 supports the periphery of the rotation
transmission member 1212a. Therefore, the supporting ball 1217
keeps a predetermined gap between the rotation transmission member
1212a and the second bevel gear 1211, and regulates the rotation
transmission member 1212a to tilt against the spindle 1213. Four
supporting balls 1217 are provided in this embodiment, however more
than three balls may be provided to make a plane.
The locking member 270 will be explained with reference to FIG. 10.
As shown in FIG. 10, a tip of the locking pin 271 is usually
positioned distantly form the engaging recess 1235 of the rotation
transmission member 1212a. When the press cap 272 is pressed
against the biasing force of the coil spring 273, the locking pin
271 is moved to be close to the rotation transmission member 1212a
and then the tip of the locking pin 271 is engaged with the
engaging recess 1235. As a result, the motion of the rotation
transmission member 1212a in the circumferential direction of the
rotation transmission member 1212a is regulated. Namely, when a
user changes the grinding disk 2, the spindle 1213 is prevented
from rotating.
A motion of the torque limiter 1210 will be explained with
reference to FIG. 11. Further, the second bevel gear 1211, the
rotation transmission member 1212a, the pressing force transmission
member 1212b and the ball 1214 of the torque limiter 1210 are only
shown in FIG. 11, the other elements such like the biasing spring
1216 and so on are not shown for convenience. Further, only one
ball 1214 is utilized for the explanation, however the motion of
the other balls 1214 is same. An arrow A in the FIG. 11(b) to FIG.
11(f) shows a rotational direction of the second bevel gear 1211.
An arrow B in the FIG. 11(c) to FIG. 11(f) shows a rotational
direction of the ball 1214.
FIG. 11(a) show one situation of the torque limiter 1210 when the
grinder 1 is not working. In FIG. 11(a), the ball 1214 is
positioned on the second cam groove 1224a, and the top of the ball
1214 is not contacted with the third cam groove 1231 of the
pressing force transmission member 1212b. In this case, as shown in
FIG. 7, the biasing spring 1216 biases and presses the pressing
force transmission member 1212b via the thrust bearing 1218,
thereby the pressing force transmission member 1212b and the top
surface of the cushion member 1215 are contact with each other, and
further the bottom surface of the cushion member 1215 and the
rotation transmission member 1212a are contact with each other.
Further, the rotation transmission member 1212a is supported by the
supporting ball 1217 and is not contacted with the second bevel
gear 1211. Further, a length of the second cam groove 1224 is
defined such that the second cam groove 1224 regulates a free
movement of the ball 1214 in the rotational direction of the second
bevel gear 1224, when the grinder 1 is not working.
FIG. 11(b) shows another situation of the torque limiter 1210, when
the rotational output of the motor 100 is transmitted to the
spindle 1213. The rotational output of the motor 100 is transmitted
to the second bevel gear 1211 thereby the second bevel gear rotates
in a direction indicated by the arrow A. Due to the rotation of the
second bevel gear 1211, the ball 1214 moves to the incline groove
1225a of the second bevel gear 1211, and contacts with the third
cam groove 1231 of the pressing force transmission member 1212b and
a wall surface 1241a in the ball holding hole 1241 of the rotation
transmission member 1212a. In this way, since the biasing force of
the biasing spring 1216 is transmitted to the ball 1214 via the
pressing force transmission member 1212b, the ball 1214 is clamped
by the incline groove 1225a and the wall surface 1241a and thereby
the ball 1214 transmits the rotation of the second bevel gear 1211
to the rotation transmission member 1212a. Namely, the second bevel
gear 1211, the ball 1214 and the rotation transmission member 1212a
rotate in an integral manner. As a result, the rotation of the
second bevel gear 1211 is transmitted to the spindle 1213. Since
the grinding disk 2 attached on the spindle 1213 is rotated, a
workpiece is worked. The part of the incline groove 1225a with
which the ball 1214 contacts is a feature corresponding to "a first
region" of the invention.
FIG. 11(c) shows another situation of the torque limiter 1210, a
transmission of rotation from the second bevel gear 1211 to the
spindle 1213 is regulated when a torque exceeding a predetermined
threshold torque exerts on the spindle 1213. In case that the
torque exceeding the predetermined threshold torque exerts on the
spindle 1213, in this embodiment, the second bevel gear continues
to rotate, however the rotation transmission member 1212a stops
rotating. Accordingly, the ball 1214 is exerted by a pressing force
which presses the ball 1214 from the rotation transmission member
1214. Due to the pressing force, the ball 1214 receives a reaction
force from the incline groove 1225a. When the sum total of a
component of the reaction force of the six balls 1214 in a
direction being parallel to the spindle 1213 exceeds the biasing
force of the biasing spring 1216, the ball 1214 contacting with the
inclined grooves 1225a rotates while pushing the pressing force
transmission member 1212b, and moves to the position where the ball
1214 contacts with the first cam groove 1223. Meanwhile, the
pressing force transmission member 1212b is biased via the thrust
bearing 1218 and is not fixed in the rotational direction, in other
word the pressing force transmission member 1212b is rotatable
freely. Accordingly, the ball 1214 moves to the first cam groove
1223 while rotating. Namely, because of the relative rotation
occurred between the second bevel gear 1211 and the pressing force
transmission member 1212b, the ball 1214 moves from the incline
groove 1225a to the first cam groove 1223 while the ball 1214 is
rolling. In this way, because the ball 1214 is positioned on the
first cam groove 1223 which is parallel to the rotational surface
of the second bevel gear 1211, the transmission of the rotation is
regulated from the second bevel gear 1211 to the rotation
transmission member 1212a thereby the torque exerted on the spindle
1213 is reduced. Further, since the pressing force transmission
member 1212b is pushed by the ball 1214, a gap between the pressing
force transmission member 1212a and the upper surface of the
cushion member 1215 is provided.
Each FIG. 11(d) and FIG. 11(e) shows another situation of the
torque limiter 1210 respectively after the ball 1214 has moved to
the position where the ball contacts with the first cam groove 1223
and the third cam groove 1231. Because of the rotation of the
second bevel gear 1211, the ball 1214 moves toward another second
cam groove 1224b which is located next to the second cam groove
1224a in the circumferential direction while the ball 1214 is
rolling. In each FIG. 11(c) to FIG. 11(e), the biasing force of the
biasing spring 1216 is transmitted to the second bevel gear 1211
from the pressing force transmission member 1212b via the ball
1214. Namely, the biasing spring 1216 always biases the second
bevel gear 1211 and the pressing force transmission member 1212b so
as to be close to each other.
FIG. 11(f) shows another situation of the torque limiter 1210 in
which the ball 1214 contacts with the incline groove 1225b, when
the ball 1214 moves from the first cam groove 1223 to the second
cam groove 1224b. On the way of the ball 1214 to the second cam
groove 1224b, the pressing force transmission member 1212b biases
by the biasing spring 1216 contacts with the cushion member 1215
again. After that, the torque limiter 1210 returns to the situation
shown by FIG. 11(b) in which the ball 1214 contacts with the
incline groove 1225a by passing the second cam groove 1214b, and
then the similar cyclic behavior of the torque limiter 1210 will be
repeated.
The rotation of the second bevel gear 1211 is not transmitted to
the rotation transmission member 1212a in FIG. 11(c) to FIG. 11(f)
respectively. Under these situations, the first cam groove 1223,
the second cam groove 1224 and the incline groove 1225b of the
second bevel gear 1211, and a part of the third cam groove 1231 of
the pressing force transmission member 1212b except a part of the
third cam groove 1231 with which the ball 1214 contacts in FIG.
11(b), is a feature corresponding to "a second region" of the
invention.
According to the second embodiment described above, since the
thrust bearing 1218 is provided, the pressing force transmission
member 1212b biased by the biasing spring 1216 is rotatable thereby
the relative rotation between the second bevel gear 1211 and the
pressing force transmission member 1212b is occurred.
Further, according to the second embodiment, because the ball 1214
moves while rolling due to the relative rotation of the second
bevel gear 1212 and the pressing force transmission member 1212b,
the ball 1214 can move smoothly. Therefore, the torque limiter 1210
works smoothly. Further, in comparison with a composition in which
the ball 1214 moves while sliding against the friction force, the
degradation or the heat generation of the ball 1214 by the friction
force is reduced.
Further, according to the second embodiment, the biasing spring
1216 always biases the second bevel gear 1211 and the pressing
force transmission member 1212b so as to be close to each other.
Therefore, when the rotation of the second bevel gear 1211 is not
transmitted to the pressing force transmission member 1212b, the
second bevel gear 1211 is regulated to rotate while tilting against
the spindle 1213.
Further, according to the second embodiment, the length of the
second cam groove 1224 in the circumferential direction is defined
such that the second cam groove 1224 regulates the free movement of
the ball 1214 in the rotational direction of the second bevel gear
1211, when the grinder 1 is not working. In case that the free
movement of the ball 1214 in the rotational direction of the second
bevel gear 1211 may not be regulated, when the grinder 1 starts or
stops driving, a rotation differences between the second bevel gear
1211 and the pressing force transmission member 1212b may be
occurred by the movement of the ball 1214. Due to the rotation
differences, an inadvertent torque may be exerted on the spindle
1213 or a failure of the driving of the torque limiter 1210 may be
occurred when the grinder 1 starts or stops driving. However,
according to this embodiment, because the length of the second cam
groove 1224 is defined such that the second cam groove 1224
regulates the free movement of the ball 1214 in the rotational
direction of the second bevel gear 1211 when the grinder is not
working, the inadvertent torque is not exerted and the failure of
the driving of the torque limiter 1210 is not occurred.
Further, according to the second embodiment, the rotation
transmission member 1212a includes the ball holding hole 1241 which
holds the balls 1214, therefore the rotation transmission member
1212a has a function for transmitting the rotation of the second
bevel gear 1211 to the spindle 1213, as well as for keeping the
interval of the balls 1214. Accordingly, another interval keeping
member for keeping the interval of the balls 1214 is not necessary,
therefore the number of the components of the torque limiter 1210
is reduced.
Further, according to the second embodiment, because the cushion
member 1215 is made of resin, an impact power generated when the
rotation transmission member 1212a and the pressing force
transmission member 1212b crash into the cushion member 1215 is
absorbed. Further, in a state that the ball 1214 is positioned on
the second cam groove 1214b, the ball 1214 does not contact with
the pressing force transmission member 1212b provided with the
third cam groove 1231, thereby the impact power is regulated to
transmit from the pressing force transmission member 1212b to the
second bevel gear 1211 via the ball 1214.
Further, according to the second embodiment, the first cam groove
1223, the second cam groove 1224 and the incline groove 1225 are
disposed on the surface of the second bevel gear 1211 opposed from
the side where the grinding disk 2 is attached. Therefore,
components of the torque limiter 1210 such as the rotation
transmission member 1212a, the pressing force transmission member
1212b, the ball 1214 and the cushion member 1215 and so on, which
are disposed to oppose to the first cam groove 1223, the second cam
groove 1224 and the incline groove 1225, are disposed on the
surface opposed to the side where the grinding disk 2 is attached
with respect to the second bevel gear 1211. Therefore, a length of
a part of the spindle 1213 protruding in a direction from the
second bevel gear 1211 toward the grinding disk 2 attached portion
is shortened, thereby the grinder 1 is downsized. Furthermore,
since the gear teeth are formed on the edge part of the second
bevel gear 1211, the recess 1220 is formed at a central part of the
second bevel gear 1211. By arranging components of the torque
limiter 1210 such as the rotation transmission member 1212a, the
pressing force transmission member 1212b, the ball 214, the cushion
member 1215 and so on at the recess 1220, each components are
rationally arranged, thereby the torque limiter 1210 is downsized.
As a result, the grinder 1 is downsized.
Further, according to the second embodiment, the gear portion 1222
is formed at an opposite side from a side to which the grinding
disk 2 is attached with respect to the longitudinal direction of
the spindle 1213. Therefore, a length of the spindle 1213
protruding from the second bevel gear 1211 is shortened, and as a
result, the grinder 1 is downsized. Further, since the gear portion
1222, the first cam groove 1223, the second cam groove 1224 and the
incline groove 1225 are respectively arranged on the opposite side
of the second bevel gear 1211 from where the grinding disk 2 is
attached, the components of the torque limiter 1210 is rationally
arranged. Therefore, the grinder 1 is further downsized.
In the second embodiment described above, the incline groove 1225
inclining the rotational surface of the second bevel gear 1211 is
disposed on the second bevel gear 1211, however it is not limited
to this composition. For example, in case that a depth difference
between the first cam groove 1223 and the second cam groove 1224 is
shorter than the radius of the ball 1214, the incline groove 1225
may be disposed as a perpendicular groove including a perpendicular
surface which perpendicular to the rotational surface.
In the embodiments described above, the biasing spring 216, 1216
always bias the flange 212 or the pressing force transmission
member 1212b, however at least in case the rotation of the second
bevel gear 211, 1211 is transmitted to the flange 212 or the
pressing force transmission member 1212b, the biasing force may be
provided.
In the embodiments described above, the second bevel gear 211, 1211
engages with the first bevel gear 200 thereby the rotational output
of the motor 100 is transmitted, however another rotational member
as "a driving rotational member" other than the second bevel gear
may be provided. Namely, the rotation of the second bevel gear may
be adapted to be transmitted to the rotational member as "a driving
rotational member".
In the embodiments described above, the length of the second cam
groove 224, 1224 in the circumferential direction is defined such
that the free movement of the ball 214, 1214 in the rotational
direction of the second bevel gear 211, 1211 is regulated, however
the length of the second cam groove 224, 1224 is not limited to
regulate the free movement of the ball 214, 1214.
In the embodiments described above, the incline groove 225, 1225,
233 includes an incline surface which inclines the rotational
surface of the second bevel gear 211, 1211 of the flange 212,
however the incline surface is not limited to incline against the
rotational surface with a predetermined angle, but may be formed as
an arc-like surface. Further, the incline groove may be provided
with a plurality of incline surfaces which incline against the
rotational surface with each angle respectively.
In the embodiments described above, the torque limiter 210, 1210
including six balls 214, 1214 respectively are explained, however
the number of the ball is not limited to six but more than three to
make a plane. Further, the roll member is not limited to the ball,
the roll member may be provided with a roller such as a cylinder
shaped member, a circular cone shaped member or a circular
truncated cone shaped member and so on.
In the embodiments described above, for convenience of explanation,
the longitudinal direction of the spindle 213, 1213 fits to the
gravity direction such that the second bevel gear 211, 1211 is
located lower in the gravity direction, however the position of the
ball 214, 1213 is different from the explanation described above
according to the situation for utilizing the grinder 1. For
example, in a state that the spindle 213, 1213 is put upside down,
when the grinder 1 is not working, the ball 214, 1214 does not
contacts with the second bevel gear 211, 1211. Namely, based on the
gravity direction and the situation for utilizing the grinder 1,
the contact relation between the ball 214, 1214 and the other
member and the contact relation between the ball retainer 215, the
cushion member 1215 and the other member may differ from the
embodiments described above.
Further, in the embodiments described above, it is explained by
utilizing the grinder 1 in which the spindle 213, 1213
perpendicular to the rotational shaft 101, however it is not
limited to these composition in which theses axes perpendicular to
each other.
In the embodiments described above, it is explained by utilizing
the grinder 1 including the torque limiter, however this invention
may be apply to a power tool except grinder, which actuates a
rotational operation, for example, it is possible to apply this
invention to a hammer drill or a circular sawing machine and so
on.
DESCRIPTION OF NUMERALS
1 grinder 2 grinding disk 10 main housing 20 gear housing 21 coil
spring engaging portion 30 wheel cover 40 rear cover 100 motor 101
rotational shaft 200 first bevel gear 210 torque limiter 211 second
bevel gear 212 flange 213 spindle 214 ball 215 ball retainer 216
biasing spring 220 recess 221 through-hole 222 gear portion 223
first cam groove 224 second cam groove 225 incline groove 230
through-hole 231 third cam groove 232 forth cam groove 233 incline
groove 234 engaging pin 235 engaging recess 240 through-hole 241
ball holding hole 250 disc spring 251 plain washer 252 nut 260 ball
bearing 270 locking member 271 locking pin 272 press cap 273 coil
spring 274 flange 280 engaging groove 281 inner flange 282 outer
flange 300 electrical wiring portion 301 power code 302 switch 1210
torque limiter 1211 second bevel gear 1212a rotation transmission
member 1212b pressing force transmission member 1213 spindle 1214
ball 1215 cushion member 1216 biasing spring 1217 supporting ball
1218 thrust bearing 1220 recess 1221 through-hole 1222 gear portion
1223 first cam groove 1224 second cam groove 1225 incline groove
1226 supporting groove 1231 third cam groove 1236 cushion member
holding portion 1241 ball holding hole
* * * * *